Fluid pressure motor



Y' a 22,1945; Rqjus 2,376,475

FLU-I'D PRESURE MOTOR Filed Sept 29. 1942 Y INVENTOR 7 R ILKinJBush ATTORNEY Patented May 22, 1945 UNITED STATES PATENT OFFICE FLUID PRESSURE MOTOR Rankin J. Bush, Jeannette, Pa assignor to The Westinghouse Air Brake Company, Wilmerding, Pa., a corporation of Pennsylvania Application September 29, 1942, Serial No. 460,050

3 Claims.

This invention relates to fluid pressure motors and more particularly to a flexible diaphragm structure for use therein.

Flexible disk like diaphragms made from rubber like composition and having molded therein suitable reenforcing fabric have been developed to withstand high fluid pressures such as encountered in certain air brake devices. Unlike ringed pistons however, the movement or deflection of such diaphragms must be limited in order to avoid overstressing of the diaphragms and consequent premature failure thereof. Where it is desired to move a device a distance exceeding the deflection of an operating diaphragm it has therefore been necessary to resort to a lever or the like to amplify the diaphragm movement and due to use of the lever a larger diaphragm has been required to provide a certain delivered force at the device than if the diaphragm would have been connected directly to the device.

The principal object of the invention is the provision of an improved diaphragm structure of the above type for connection directly with a device to be actuated and so constructed as to provide any desired movement of said device without overstressing the diaphragm structure.

According to this object, I provide a structure including a pile of diaphragms of the above described type, the sum of the deflections of which equals the desired movement of the device to be operated. I connect these diaphragms to each other in series with the central portion of the diaphragms at one end of the pilefixed against movement and the corresponding portion of the diaphragm at the opposite end bearing against the piston head to be operated. In case the pile comprises only two diaphragms the outer peripheries thereof are connected to provide an air tight seal therebetween. In case the pile comprises more than two diaphragms the outer peripheries of each adjacent pair of diaphragms are thus connected together while the inner peripheries of each adjacent pair, not including the end diaphragms, are also connected to provide an air tight seal between them. The space within the diaphragms is arranged to receive fluid under pressure to extend the structure in a direction away from the end diaphragm having the fixed central portion and to apply actuating force through the other end diaphragm to the connected piston head. With this structure the piston head may be moved a distance equal to the sum of the permissible deflections of all of the diaphragms.

I am aware that various metal diaphragm structures, such as of the corrugated type, have been developed wherein overstressing of the in-. dividual corrugations may be avoided by providing an adequate number of corrugations to obtain a desired movement. I am also aware that corrugated tubing or bellows made of rubber composition and fabric is old. So far as I am aware however a rubber fabric diaphragm structure, of what may be called the corrugated type, which will withstand high fluid pressures has never been produced due I understand to it being impossible to provide in such a structure the required fabric reenforcement.

This difliculty is avoided however according to the invention since the improved diaphragm structure is built up from a multiple of individual disc like diaphragms of a type known to withstand high pressures.

Other objects and advantages will appear from the following more detailed description of the invention.

a In the accompanying drawing; Fig. 1 is a cross-sectional view of a fluid motor embodying a diaphragm structure constructed in accordance with the invention; and Fig. 2 is a view similar to Fig. 1 but of another embodiment of the invention.

Description Figure 1 The fluid motor shown in Fig. 1 comprises a casing I having two axially aligned bores 2' and 3 of difierent diameters connected at their adjacent ends and open at their opposite or outer ends. The outer end of bore 2 is closed by a cover 4 having an annular boss 5 extending inwardly from its inner face. In the outer end of bore 3 is disposed an adjusting nut 6 having an adjustable screw-threaded connection with the casing.

A piston-head l disposed in the bore 2 is supported on the end of a piston rod 8 which is slidably mounted and supported in a suitable axial bore provided through the nut 6. The outer end of the rod 8 is adapted to be connected to any device, (not shown) which it is desired to operate. A coil spring 9 encircling the piston rod 8 within bore 3 bears at one end against the nut 5 and at the opposite end against an annular collar l0 provided around the piston head 1.

According to the invention 1 provide an improved diaphragm structure for applying force to the piston head 1 for moving said head and the rod 8 in a direction against spring 9 to actuate the device connected to the rod.

In the embodiment shown in Fig. L this improved diaphragm structure comprises two ir dividual disc like flexible diaphragms II and I2 of smaller diameter than bore 2 and disposed therein. Both of these diaphragms are constructed of any suitable material such as rubber composition having embedded therein suitably disposed fabric or the like to support the diaphragm against relative high fluid pressures acting on one face.

The diaphragm II has a central opening through which extends a projection I. boss 5, said projection being of smaller diameter than said boss to provide an annular shoulder on the end of said boss for engagement by one side of the portion of diaphragm II immediately adjacent and surrounding the periphery of said opening. This central portion of diaphragm H is clamped into leak tight contact with the end of boss I by a nut ll having screw-threaded contact with the projection I3.

The central portion of the diaphragm I2 is disposed in operative engagement with the piston head 9. This diaphragm may be identical to the diaphragm II if desired and hence be secured to the piston head I in any conventional manner, but I prefer that the central portion of diaphragm I2 be imperforate as shown in order to minimize the possibility of leakage of fluid under pressure from one side of the diaphragm to the opposite side. The projection I3 may be of such length as to engage the diaphragm I2 for limiting movement of the piston head under the action of spring 9.

The outer peripheral edges of the two diaphragms are connected together to prevent leakage of fluid under pressure therebetween. The

connecting structure may comprise a rigid ring Iii of the same outside diameter as the two diaphragms interposed between and engaging the adjacent sides of the two diaphragms near their outer edges. A second rigid ring l6 encircling the ring it and the two diaphragms has at one end an inwardly extending annular collar engaging the outer face of diaphragm II over a portion opposite that engaged by ring IS. The corresponding portion of the outer face of diaphragm I2 is engaged by a ring I! against which bears a nut l8 having a screw-threaded connection with ring it interiorly thereof. The nut I8 is screwed against the ring II with such force as to obtain leak tight connections with the opposite sides of the two diaphragms.

The two diaphragms and ring I! cooperate to form between the diaphragms a pressure chamber [9 which is open through a radial port ill in projection I3 to an axial bore 2| extending through the boss to the exterior of cover A. The outer end of this bore may be screw-threaded as shown in the drawing to receive one end of a control pipe through which fluid under pressure may be supplied to and released from pressure chamber I9.

In use, with pressure chamber I! at atmospheric pressure the spring 9 may be so adjusted by nut 6 as to exert a force on piston head I to urge said head and thereby the diaphragm structure to the position shown and deflned by contact between diaphragm l2 and the end of the extension ll of boss I.

If fluid under pressure is now supplied through bore 2| to chamber 9 it acts on the diaphragm II to apply force to the piston head I in opposition to that of spring 9 and when this force becomes suflicient to overcome said spring it will move the piston head I in the direction of bore 3. As the piston head thus moves. the consequent movement of the contacting portion of diaphragm I2 creates a stress in the portion between said head and the outer peripheral portion of said diaphragm which tends to move the diaphragm connecting rings l5 and I6 with the piston head, but such movement of said rings is opposed by the resistance to deformation of the portion of diaphragm I I between said rings and boss I. When however the stress in diaphragm I2 is increased to a degree exceeding the resistance to deformation of diaphragm II, the diaphragm I2 will pull the rings I5 and I8 and the connected portion of diaphragm II in the direction of bore 3 and this will continue as long as the piston head I continues to move and thus maintains a stress in diaphragm I2 exceeding the resistance to deformation of diaphragm I I. Since the resistance to deformation in diaphragm l I will increase substantially as the stress in diaphragm I2 increases upon movement of piston head I it will be seen that the two diaphragms will both deflect to substantially the same extent, as a result of which the rings l5 and I6 will move only substantially one half the movement of the piston head I. Movement of the piston head I may be limited by engagement with the end of the adjusting nut 8 at which time further deflection of the two diaphragms will cease.

From the above description it will now be seen that both diaphragms bend or deflect upon movement of the piston head I and that the combined deflection of the two diaphragms therefore equals the stroke of said piston head. If the resistance to deformation of the two diaphragms are identical the deflection of each will equal one half the stroke of the piston head. In case the resistances head I is twice the permissible deflection of either one of the two diaphragms, the combined deflection of the two diaphragms will provide for full stroking of the piston head without overstressing either diaphragm.

If desired each of the diaphragms Ii and I! may be of the well known high pressure type having an annular corrugation 22 connecting the central portion of the diaphragm to its outer portion and projecting beyond the low pressure side of the diaphragm in order to provide for greater deflection and less stressing of the structure than obtainable with the type not having such a corrugation. As applied to the structure shown in Fig. 1 the corrugations 22 of the two diaphragms project from the outer and opposite faces of the respective diaphragms since the adjacent faces are the high pressure faces arranged to be subjected in chamber I9 to pressure of fluid.

The outer surface of ring I6 is in the shape of the segment of a sphere formed at a radius only slightly less than that of bore 2 in the casing, so that the ring will slide in the casing and also engage the wall of said bore to support the weight of said ring and of ring I5 and nut l8. Possible sagging of the diaphragms, which might occur if the diaphragms carried the weight of these parts, is thus avoided to maintain the diaphragms operative at maximum efliciency.

As above described the ring It moves in bore 2 upon movement of the piston head I. The spherical shape of the outer surface of ring is is provided to prevent said ring becoming bound in If greater movement of a, piston head is required than provided by the combined permissible deflections of two flexible diaphragm, as obtained in the structure shown in Fig. 1, the number of diaphragms employed may be increased, preferably in multiples of two, to a degree where their combined permissible deflections equals at least the requlredstroke of the pistonhead, as provided for in the structure shown in Fig. 2 which will now be described. i

The structure shown in Fig. 2 comprises 9. casing 25 having a bore 29 closed at one. end by a cover 21 having an inwardly extending boss 28. In this chamber are four flexible diaphragms 29, 39, 3| and 32 of the same structure as the dia phragms II and I2 above described. The diaphragms 29 and 30 constitute one pair and the corrugations 22 therein are oppositely arranged as in Fig. 1. The diaphragms 3| and 32 constitute a second pair and the corrugations 22 therein are also oppositely arranged.

The central portion of diaphragm 29 isclamped against the end of boss 28 in leak tight contact i by a collar 33 provided on one end of a sleeve 34 which is mounted ma bore through said boss and on the outer end of which is screw-threaded,

The outer peripherial portions of diaphragms.

29 and 39 are operatively connected together by rings 38, 39, and 40 and a nut 4| like the structure shown in Fig. 1, while corresponding rings "42, 43, and 44 and a nut 45 operatively connect the outer peripherial portions of diaphragms 3| and 32 together. The two clamping rings 39 and 43 are slidable in bore 25 and their outer surfaces are spherical in form to prevent the rings becoming bound in said bore in case the rings should rock in the bore.

A sleeve 46 extends through the central bores in the two intermediate diaphragms 3n and 3| and has at one end an annular collar 41 bearing against the high pressure side of the diaphragm 3|. A sleeve 48 is slidably mounted on sleeve 46 between the two diaphragms 3B and 3| and bears against the adjacent and low pressure faces thereof. Mounted on the opposite end of sleeve 45 is a ring 49 engaging the. high pressure face of diaphragm 3|] and a nut 50 having screw-threaded contact with said sleeve and tightened against the ring 49 for thereby clamping the central portions of the two diaphragms between the opposite ends of sleeve 48 and the collar 41 and ring 49.

The sleeve 34 has an axial passage open at its outer end to a screw-threaded bore 52 provided to receive one end of a control pipe. The opposite end of passage 5| is open to a passage 52 extending through the sleeve 46. Adjacent the sleeve 34 the sleeve 46 has a radial passagechambers 54 and 56 are open to the atmosphere by way of passages 53 and 55, respectively, and

thence throughpassages 52 and II, the piston head 36 will urge the diaphragm 32 inztoccntact with the adjacent end of sleeve 46 and the opposite end of said sleeve against the adjacent end of sleeve 34 which is fixed in the boss 23.

If fluid under pressure is supplied to passages 5| and 52 and thence through ages 53 and 55 to pressure chambers 54 and 56 respectively, such pressure acting in chamber 54 on diaphragm 3| will. tend to move same. away from diaphragm 29 which is flxed centrally to the casing, and this tendency is opposed and balanced by the pressure of fluid in chamber 55 acting on the diaphragm 3|. The pressure in chamber 59 acts on the diaphragm 32 in opposition to the force of spring 31, and when such pressure becomes in- 53 connecting passage 52 to a pressure chamber creased sufficiently to overcome said spring, the

diaphragm 32 will be deflected thereby and urge the piston head 36 toward the left hand. As the diaphragm 32 is thus deflected a stress will be created therein and when this stress slightly exceeds the resistance to deformation of diaphragm 3|, the latter will deflect about it's cen-, .tral portion in the same direction.

phragm 32 will as a result become stressed and when thedegree of such stress transmitted through sleeves 46 and 49 to the central portion of diaphragm 30 exceeds the resistance to deformation thereof, the diaphragm 39 will yieldat its central portion and create a stress therein which will finally cause deflection of the diaphragm 29 about its central portion which is clamped to the casing.

From the above it will be noted that each of the diaphragms 29 to 32 will yield or deflect upon movement of the piston head 36, and that the sum of the deflections of the several diaphragms will equal-the extent of movement of the piston head.

When the piston head is being moved under pressure of fluid in chamber 56, the deflection of the leading diaphragm may be greatest due to having to cause deflection of all of the other diaphragms, whilethe deflection of the other diaphragms will beless in the direction of diaphragm 29 the deflection of which may be the least. When the force of spring is increased to a degree which counterbalances the pressure of fluid in chamber 56 and the piston head 36 stops moving, the stress in the several diaphragms will equalize, and assuming the characteristics of the several diaphragms to be identical, the deflection of each will equal substantially one fourth of the distance moved by the piston head 36.

In case the resistances to deformation of the several diaphragms differ, then there will be slight variations in the deflection of the several diaphragms, as will be apparent. Regardless of this however, the sum of the deflections of the several diaphragms will equal the stroke of the piston head; and with the characteristics of the diaphragms used known, an adequate number may be employed to prevent overstressing-any of the diaphragms.

Summary From the above it will now be seen that I have provided a diaphragm structure which is practical for use with high-actuating pressures since it provides for desired .movement of a device to be operated without overstressing the diaphragms.

The diaphragms are of a high pressure type and are serially connected to obtain a movement of The die-- the device equal to the sum or the deflections of the several diaphragms. Any desired number oi. diaphragms may be employed as required to obtain a desired movement, and regardless of the number the deflection or each individual diaphragm will be substantially the same and will not exceed the permissible value to avoid overstressing.

Having now described my invention, what I claim as new and desire to secure by Letters Patent, is:

1. A fluid motor comprising a casing having a horizontally arranged bore. a horizontally movable piston head in said casing, a pile of individual axially aligned non-metallic disc like flexible diaphragms disposed in said bore in concentric relation therewith, each diaphragm comprising a central portion, a peripherial portion and an annular corrugation connecting said portions and providing for movement 01' said portions axially relative to each other, the central portion of the diaphragm at one end of said pile being connected to said piston head for moving same when subject on one face to pressure oi fluid and the central portion of the diaphragm at the opposite end of said pile being supported by said casing, means including ring-like means connecting the peripherial portions oi said diaphragms together to provide between the diaphragms space to receive fluid under pressure to act on said one diaphragm for moving said piston head, and means providing for supply of fluid under pressure to said space, the surface of said ring like means having sliding contact with the wall of said bore and being formed lengthwise of said bore on a radius equal substantially to the radius of said bore.

2. A fluid motor comprising a casing having a horizontally arranged bore, a horizontally movcentral portion of the diaphragm at the opposite o end of said pile being supported by said casin ring-like means securing the peripherial portion of the diaphragm engaging said piston head to the peripherial portion of the adjacent diaphragm and providing an air tight connection therebetween, other ring-like means connecting the peripherial portion of the diaphragm supported by said casing to the peripherial portion of the adjacent diaphragm and providing an air tight connection therebetween, still other means connectmg the central portions or the two said adjacent diaphragms together and providing an air tight connection therebetween, the last named means and the two ring-like means cooperating with said diaphragms to provide a fluid receiving space extending between the two end diaphragms and in between each pair or diaphragms connected by the said ring-like means for receiving fluid under pressure to act on the diaphragm connected to said piston head for moving said piston head, means providing for supply of fluid under pressure to said space, both oi. the above mentioned ring-like means having an exterior surface in sliding contact with the wall of said bore and being formed axially of the ring on a radius equal 1 substantially to the radius of said bore.

3. In combination, a casing having a horizontally arranged bore, two spaced apart axially aligned non-metallic diaphragms disposed in said bore in concentric relation therewith, each diaphragm comprising a central portion, a peripheral portion and an annular corrugation connecting said portions means securing the central portion of one of said diaphragms to said casing, an element to be moved by deflection of said diaphragms secured to the central portion of the other diaphragm, means including a ring-like member interposed between and securing the peripheral portions of the two diaphragms together, said means and diaphragms cooperating to form a pressure chamber between said diaphragms, and means connected to said chamber providing for supply of fluid under pressure to and release of fluid under pressure from said chamber for controlling d5 deflection of said diaphragms the outer peripheral surface of said ring-like member having sliding contact with the wall of said bore and bein formed lengthwise 01' said bore on a radius equal substantially to the radius of sa d bore.

RANKIN J. BUSH. 

